Transmission and control mechanism



Oct. 31, 1939. w. SENGER r AL I 2,178,439

TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 1 Oct. 31, 1939. w. SENGER ET AL 2.178.439

TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 2 INVENTORS Q P ATTORNEY.

Oct. 31, 1939. w $ENGER ET AL 2,178,439

TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 3 IN VENT 01? S AT T ORNEY Oct. 31, 1939. w. l. SENGER ET AL' 73. 39

TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 4 INVENTORS ATTORNEY.

Oct. 31, 1939. w. I. SENGER ET AL TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 5 INVENTORS ATTORNEY.

Oct. 31', 1939. w. SENGER ET AL TRANSMISSION AND CONTROL MECHANISM Filed June s, 1936 9 Sheets-Sheet 6 ATTORNEY.

Oct. 31, 1939. w. l. SENGER AL 2,173,439 I TRANSMISSION AND CONTROL MECHANISM Filed June 3, 1936 9 Sheets-Sheet 8 ATTORNEY.

' Oct. 31, 1939. w. 1. SENGER ET AL 2,178,439

TRANSMISSION AND CONTROL MECHANISM Filed June 3-, 1936 9 Sheets-Sheet 9 ATTORNEY.

Patented Uct. 31, 139

TRANSIVHSSllU-N AND CONTROL MECHANISM Werner Irving Senger and Vigo von Krogh Sundt, Madison, Wis, assignors to Gisholt Machine Company, Madison, Wis.

Application June 3, 1936, Serial No. 83,306

21 Claims.

This invention relates to transmission and the required elements to change from any availcontrol mechanism for machine tools, etc., and more particularly for the spindle transmission of a lathe.

A purpose of the invention is to provide an improved mechanism, for a mechanical transmission having alternative driving or interrupting means, which will eiTect a period of less than full driving capacity of the driving-interrupting means during engagement thereof, as for instance to avoid shock upon starting or reversing a spindle transmission in a machine tool, or to assist the engagement of sliding gears or clutches of a spindle transmission.

A further purpose of the invention is to provide improved and more conveniently operated mechanism for controlling of various elements of a transmission, as for instance a rate changer,

a clutch or revcrser, and a brake.

A further purpose is to provide an improved transmission mechanism in which rate changes and other control operations may be efiected by power.

A further purpose is to provide an improved interlocking or inter-related operation of power operated shifting devices for controlling transmission effects of various sorts, as for instance rate change, interruption, reversal and braking.

A further purpose is to eiiect an improved control for a transmission having a rate changer and other adjustable control devices, as for instance, a reverser, a brake or an interrupter, in which for the purpose of effecting a rate change there is an inter-related operation of the rate changer and one or more of the-other devices, but for other control purposes there is an independent operation of some of the other devices.

A further purpose is to effect an improved rate change device in which, as an incident to rate changing, the power transmission to the rate changer is automatically interrupted before adjusting the rate changer, and automatically connected again following completion of the rate change.

A further purpose is to provide an improved control mechanism for asrate changer having a reversible driving connection, in which the driving connection is interrupted prior to the shifting of the rate changer, and is connected, following the rate change, to drive the rate changer in the same direction as before.

A further purpose is to provide an improved shifting device for a rate changerhaving a serial arrangement of shiftable rate change elements or groups of elements, in which the shifting of able rate to any other available rate will invariably proceed in a sequence such that the elements or groups will be shifted one at a time in a preferred order.

A further purpose is to provide an improved device for control of a rate changer productive of a relatively large number of different rates, in a manner such that selection of a'dcsired rate may be instantly made irrespective of the preceding rate and the shifting to effect the selected rate will be selectively performed without effecting position combinations productive of other rates.

A further purpose is to improve and simplify the mechanism of the co-pending application Serial No. 24,201, filed May 31, 1935, in a machine operative for similar purposes. In part the improvements here shown reside in improved operationyin part in an improved structure of the parts and the relationship thereof and in part in improved simplicity and convenience of manufacture, assembly and operation.

A further purpose is generally to simplify and improve the construction, operation and relationship of transmission and control mechanism of a machine tool, particularly when the transmission includes reverser or interrupter devices, a brake device and a rate change device; and still other objects will be apparent from this specification.

The invention consists in the construction and arrangement of parts as herein illustrated, described and claimed, and in such modifications thereof as are equivalent to the structure claimed.

Throughout the specification the same reference characters have been used to indicate the same parts, and in the drawings:

Figure 1 shows a front view of a headstock and spindle drive portion of a lathe in which the invention is incorporated.

Figure 2 is a left end elevation of the same structure.

Figure 3 is a vertical section, taken approxi- Figure 6 is an enlarged vertical section showing a spindle brake, taken approximately along line 6-6 of F18. 1.

Figure 7 is an enlarged horizontal section of a controller unit taken approximately along line of Fig. 5.

Figure 8 is a vertical section of the same controller unit and associated structure, taken approximately along line 66 of Fig. 7.

Figures 9, 10, 11, 12, 13, 14 are vertical sections of the same controller unit, taken respectively along lines 9--6, |5|6, |2-|2, |3|3 and |4|4 of Fig.7.

Figure 15 is a more or less diagrammatic view showing certain control mechanism of the machine and certain interconnections thereof.

Figure 16 is' a perspective view of a speed change controller.

Figures 17, 18 are partial sections showing respectively top and side views of a pressure delay device associated with the rate change piston devices.

Figure 19 is a vertical section of a control device associated with the spindle reverser.

The machine of the drawings is a lathe, which includes a bed, a portion of which is shown at I, Fig. 1. upon which a headstock, generally denoted by the numeral 2, is mounted. A spindle 3, Figs. 1, 4, is driven from a power source associated with the machine, in this case a drive pulley 4. The lathe has suitable tool supports, not shown, driven through a feed train which may be any of several well known types driven from the "spindle 3 through a feed gear such as 5, Fig. 4. Spindle transmission mechanism is provided for driving spindle 3 from pulley 4 at a variety of rotational speeds, the transmission being of improved form and arrangement as more particularly pointed out in a co-pending application, Serial No. 117,305, filed December 23, 1936. The spindle transmission includes the pulley 4, a reverserinterruptor generally denoted by the numeral 6, Fig.4, and a rate change device generally denoted by the numeral 1, the pulley, reverser, rate changer and certain other mechanism being unitarily carried by a removable housing member 6, Figs. 2, 4, which is rigidly fixed with an upstanding housing portion 6 carried by bed I, in which spindle 6 is rotatably mounted, as more particularly described in said co-pending application Serial No. 117,305.

The reverser-interrupter 6 is of the following construction: Pulley 4, Fig. 4, is fixed on a shaft II which carries a plurality of outer clutch members H, H each independently rotatable and respectively keyed with the alternate driven plates of different friction plate groups l3, H of different driving clutches each having alternate driving plates keyed to an inner member |5 which is slidably keyed on shaft ID. The member drives a shaft l6 through meshed gears I6. Member |2 drives shaft |6 through double sprockets I6, 26, the sprockets being connected by drive chains such as 2|, Fig. 3. The inner member |5 provides an annular abutment portion 22, and is axially shiftable to alternatively cause frictional engagement between the plates of group I3, or oppositely to cause engagement of the plates of group I4, and the arrangement is such that as member I5 is shifted in opposite directions the shaft I6 is driven in forward and reverse directions.

The spindle rate changer is constructed as follows: A shaft 23, Fig. 4, is driven from shaft l6 through a rate change device which includes the gears 24, 25, fixed together and slidably keyed on shaft l6 and respectively engageable one at a time with gears 21, 26, 26 which are fixed on shaft 23. A shaft 36 is driven from shaft 23 through a rate change device which includes the gears 3|, 32, 33 fixed together and slidably keyed on shaft 36 and respectively engageable one at a time with a gear 34, the gear 26 and another gear 35, each of the gears 34 and 35 being also fixed on shaft 23. A gear 36 is fixed on a sleeve 36a which is rotatably supported on the extended end 36a of shaft 36, sleeve 36a and gear 36 being driven from shaft 36 through a rate change device which includes a clutch gear 31 shiftable to engage internal clutch elements 36b on sleeve 36a, in which case gear 36 is driven at the same speed as the shaft 36, or to engage gear 36 of a reduction train consisting of gear 36, a shaft 36 co-axial with the shaft 23, and a gear 40 which meshes with gear 36, in which case gear 36 is driven at relatively slow speed. The gear 36 drives spindle 3 and feed gear 5 through a meshed gear 4| fixed on the spindle, and the several rate change devices and the reverser provide for eighteen changes of rotational spindle speed, substantially in a geometrical progression, and in either direction.

A spindle brake device generally denoted by the numeral 42, Fig. 6, includes a brake drum or friction wheel 43, Figs. 4, 6, a friction band 43a anchored at the one end with a stud 44 and normally urged toward released position by a spring 45 acting on an abutment member 46 which is fixed to the band.

The reverser 6, the various rate change units, and brake 42 are provided with means for this power operation including fluid operable piston devices as follows:

A reverser piston device for reverser 6, generally denoted by the numeral 41, Figs. 4, 15, includes a fluid operable piston 46, a cylinder 46, and a piston rod 56 provided with a coupling unit 5| which engages the enlarged end 52 of a shifter rod 53 slidable in an axial bore of the shaft ll, rod 53 being extended to carry a shifter member 54,. Fig. 4, which extends radially outwardly through suitable slots in the shaft III to engage at its ends with the slidably keyed reverser clutch member I5, whereby, as piston 46 is shifted, the abutment portion 22 of the member I5 is correspondingly shifted to operate the reverser 6. The coupling unit 5| includes a thrust bearing 5|a and suitable thrust plates 5|b, 5| fixed on piston 56 and engaging the outer race, there being suitable means, as rod |d preventing rotation of the thrust plates.

The piston 48 of reverser piston device 41 may be alternatively operated in the one or the other direction, whereby to engage the reverser 6 for forward or reverse rotation, by fluid pressure from suitable ports 56, 51, Fig. 4. Fluid pressure is continuously supplied to piston device 41 from a port 56 which continuously tends to shift reverser 6 to its central or non-engaged position, the pressure from port 56 acting at the one end of the device against an extended portion 59 of piston rod 50, and at the other end of the device against a shouldered sleeve 66. Whenever fluid pressure is applied through either port 56, 51 the piston 46 and rod H! are shifted against the resistance of the fluid pressure from port 56 by reason of the relatively large area of piston 46, but when pressure is released from bot ports 56, 51 the piston device 41 and reverser 5 will immediately be shifted to central non-driving position, the fluid from port 56 then simultaneously forcing the sleeve 6|! to the right against a shouldered a l-(ii tor-ion 8%, and, forcing the piston r011 to the left until the piston rests against the end of sleeve 60.

A spindle brake piston device, generally denoted by the numeral 6|, Figs. 7, 15, includes a piston 6|a, having a rod 62, Figs. 6, '7. Piston 6m may be forced to the left in Fig. 7, as will be later explained, to overcome spring 45 and engage brake 42, or may be forced in the other direction to permit spring 45 to release the brake.

For the speed change device comprising the shiftable gears 24, 25, 26, Figs. 4, 15, there is provided a shifter including a piston device generally denoted by the numeral 63, Figs. 8, 15, which includes a piston 63a, upon the piston rod 635 of which is fixed a shifter arm 63c engaging a suitable annular groove in the gear unit.

For the speed change device comprising the shiftable gears 3|, 32, 33, Figs. 4, 15, there is provided a shifter including a piston device generally denoted by the numeral 64, Figs. 8, 9, 15, which includes a piston 64a, upon the piston rod 841) of which is fixed a shifter arm 64c engaging a suitable annular groove in the gear unit.

For the speed change device comprising the shiftable clutch gear 31, Figs. 4, 15, there is provided a shifter including a piston device generally denoted by the numeral 65, Figs. 8, 12, 15, which includes a piston 65a upon the piston rod 65b of which is fixed shifter arm 65c engaging a. suitable annular groove in the hub of the gear.

For the operation of the several piston devices a pressure fluid source, such as a pump of any suitable type, as indicated at 69, Fig. 15, is driven whenever pulley 4 is running, as for instance by a gear 10, Fig. 4, fixed on shaft 10, the pump drawing oil from a sump 69a, diagrammatically shown in Fig. 15 which may, for instance, be formed by the lower portion of the spindle gear housing. Excess oil and waste from operation of the shifters is used to lubricate the transmission. The pressure of the fluid for the several piston devices is maintained constant by providing pump 69 with excess capacity, and by providing a constant pressure relief valve 69b, Fig. 15, as of suitable type. Excess fluid from valve 69b may be'distributed through lubricating channels (not shown) and returned to the sump.

Control means for the operation of the various piston devices is provided as follows:

A speed selector device, generally indicated by the numeral 1|, Figs.'3,, 16 is similar to that shown in a co-pending "application, Serial No. 58,549, filed January 10, 1936, which will therefore, here be only briefly described. The selector device includes a fixed indicator pointer 12 against which a plurality of charts or scales are readable. One of the charts includes numerals such as 13 arranged on the exposed peripheries of flange members 14, 15 which are both fixed for rotation with a shaft 18. The numerals I3 are arranged in consecutive order and correspond with the rotative speeds available for spindle 3 upon operation of the several rate change devices to their various position combinations. Another chart readable against indicator 12 includes numerals such as H arranged on the periphery of an anifiilar member 18 which is frlctionally held to be normally rotatable with the flange members l4, 15, but is adjustable relative thereto by the means of a handle 19 which projects through a slot 80 in the member 15. The numerals indicate different work diam eters within the speed range of the machine and arranged in consecutive order.

Still another chart includes numerals such as 8|, arranged in consecutive order on the face of the member 18 to be visible through slot 89 and readable against an indicator pointer or arrow 82 which is rotatable with shaft IS. The numerals of the last mentioned chart are arranged to indicate surface or peripheral speed on the work piece rotating with the spindle.

As illustrative of the use of thespeed selector. device there is selected on the chart-8| a desired peripheral speed suitable for the turning tool used and for the work material to be operated upon, the member18 being turned by lever 19 until that peripheral speed is indicated against the pointer 82. Shaft 16 is then turned in either direction by the means of handles such as 83 until thediameter of the work piece as listed on the chart I1- is indicated against the pointer I2. If this does: not exactly correspond to an available rotational speed, as indicated on chart 13 then choice must be made of a slightly higher or lower rotational speed, the rotative speed thus selected being aligned with pointer 12, whereupon the shifter devices, later described, will shift the rate change devices to effect the desired speed.

The positioning of the selector device, as described effects the selected speed by the means of mechanism as follows:

Shaft 16, Fig. 3, is coupled for rotation with a co-axial shaft 84, Figs. '7, 8 by the means of an axially disengageable tongue and slot coupling indicated at 85, Fig. 8. Fixed on shaft 84 are a plurality of cam members 86, 81, 88, 89, 90, 9|, 92, 93, Figs. 8, 15 separated by spacers such as 94, 95, to operate various poppet valves which control the shifting of the piston devices to effect rate changing.

Thus, for controlling the movement of the piston device 63 the cams 81, 88, 89, Figs. 8, 15 respectively operate the poppet valves 81a, 88a, 89a. For, piston device 64 the cams 90, 9|, 92 operate poppet valves 99a, 9|a, 92a and for piston device 65 the cam 93 operates both the poppet valves 93a, 93a. Ineach instance the configuration of the cams is' such that as shaft 84 is rotated one only of the poppet valves of each piston device is opened by the cams in each angular position of the shaft 84 corresponding to the points where the different rotative speed indicating chart numerals 13 read against the indicator pointer 12. In each such positions the cams are cut away to permit the fluid pressure to close the other valves of the set against their seats. It will be understood that in the drawings the cams are more or less diagrammatically shown, but it will be obvious that in each device the cams may be formed to operate as just described.

The different poppet valves of the piston devices 83, 64, 65 each communicate with a different port of the associated piston device, the ports being spaced in the direction of piston movement according to the different piston positions required. Opening the poppet valve results in movement of the piston of the device to a position corresponding to the port leading to the open valve, whereby to shift the speed change units to the indicated speed position. As illustrative of this action the operation of the piston device 94 is as follows:

Referring to Figs. 9, 10, the piston device 64 has ports 98b, 9|b, 925 respectively controlled by poppet valves 99a, 9|a, 92a through suitable channels. In each instance opening the poppet valve will provide a fluid drain for the port. The ports are spaced in accordance with the three positions required for the piston 84a. Fluid is supplied to the piston device through a channel groove 91b and a-valve member 98 which may move axially in either direction. In the one direction of movement valve 98 seats against a member 99 to prevent flow of fluid from channel 912; to a groove I00 which communicates directly with port Sit), and with the poppet valve 9Ia through a channel I00a. In the other direction of movement valve 98 seats against a member III to prevent flow of fluid to the port 921) and to poppet valve 92a through the channels IOIa, IOIb. Thus if either poppet valve 9Ia or 920. is opened the resulting'reduction of pressure moves valve 08 in the direction of the opened poppet valve, and holds it in position closing the flow of fluid from supply channel 911) to the open valve. This leaves the one end of piston 64a connected to the pressure supply, and the other connected to the open poppet valve. The piston will therefore move in the direction of the open valve, thereby shifting the associated gear unit. Port 00b communicates with poppet valve a through a groove I02, Figs. 9, 10, and channels I02a, I02b, and, similarly to the operation just described, the opening of poppet valve 90b when piston 64a is in either extreme position, relieves the pressure on one end of the piston, whereupon the pressure on the other end moves the piston until the piston covers the port 901) leading to the open poppet valve.

The spacing of the ports 90b, 9Ib, 92b is such that, accordingly as the one or the other of the poppet valves is opened the piston 64a will move to three positions, corresponding to the three speed productive positions of the gears 3i, 32, 33, accordingly as the cams 90, BI, 92 open the one or'the other of the poppet valves 90a, 9Ia, 92a.

The piston device 03 isconstructed similarly to the device 64, just described and is similarly moved to three positions, corresponding to the three positions of gears 24, 25, 26, accordingly as cams 81, 88, 09 open poppet valves 81a, 08a, 00a. Since the connection and operation is substantially the same as the device 64 it will not be described in detail.

The piston device 65, Figs. 12, 15 is also similarly controlled for movement to the two positions of the clutch gear 31 by the means of fluid supplied from a channel 910, accordingly as cam 93 opens the one or the other poppet valve 93a, 93a, but in this instance, the piston 65a having only two positions, only two ports are required, as shown at 93b, 93b, Figs. 12, 15.

The various poppet valve cams associated with piston devices 53, 64, 65 are so conflgurated and positioned that as shaft 84 is rotated the various piston devices and speed change elements are moved to different position combinations resulting in speeds arranged in numerical order, and at points in the rotation of the shaft corresponding to the position of the rotation chart numerals 11 as they are successively readable against indicator 12. This results also in the arrangement of the numerals of the other charts in numerical order, the spacing thereof being determined by the spacing of the numerals on the rotation chart.

Means are provided to prevent the shifters from starting to move as the selector shaft 84 is rotated to pass through one or more positions corresponding to undesired speeds. To effect this result and other results later mentioned there is provided a delay device, generally denoted by the numeral I03, Figs. 11, 15. The cam 86, Figs. 8, 11, 15 is provided with notches such as 06a, corresponding in number and position to the speed positions of selector shaft 84. The notches 86a are normally engaged by a fluid pressed detent plunger I04, yieldably holding the cam and shaft in the various speed positions, both to mark the speed position for the operator, and to locate the cam relative to a poppet valve I05, the plunger I04 being continuously supplied with fluid from source 69, as by a pipe channel I06, and communicating channels I05a, I061), I060.

The delay device I03 includes a piston plunger I01 and a piston plunger I08 of relatively smaller area. The left end, Fig. 11, of piston I08 is continuously supplied with fluid through the channels I06, I06a. The right end of piston I01, Fig. 11, is supplied with fluid from channel I06 through an adjustable needle valve device I09 and a channel I09a. The pressure acting on .the right hand end of piston I01 normally forces both pistons I01 and I00 to the left in Fig. 11, to a position where a port I I0, which is continuous ly supplied from channel I06a, communicates with an outlet port III, through an annular groove III in piston I01. nected to a channel 81 through a groove IiIa to supply fluid to the shifter devices 63, 64, 65 as later described, but when the poppet valve I05 is opened by cam 86 during rotation of selector shaft 84 to effect a change in speed, the fluid pressure on piston 01 is immediately relieved and piston I08 forces piston I01 to the right, to the position shown in Fig. 11, and in this position the supply port H0 is cut off from port III, and port III and channel 01 are connected to a drain channel I I4. Piston I01 will almost immediately again move to the left to close the drain and again supply fluid to port III and channel 91, but only after needle valve I09 has permitted suflicient fluid to move the piston to flow therethrough. The interval of delay may be varied by adjustment of the needle valve I 09, but is suflicient that in rotating shaft 84 at normal adjustment speed no pressure will be available in channel 91 for operation of the piston devices 63, 04, 45 until the selector shaft comes to rest in a desired speed position.

The reverser piston device 41, Figs. 4, 5, 15 may be controlled to shift reverser 6 into the one or the other direction position by the means of a hand lever H5, Figs, 3, 16, fixed on a sleeve IIG, Figs. 3, 8, which is co-axial with shafts 16, 8d and coupled with a co-axial sleeve II'I, Fig 8, by the means of a tongue and slot coupling connection H8. Fixed on sleeve H1 is a rotary valve member H8, Figs. '1, 8 having an annular fluid channel I20, Figs. 8, 14, which is supplied with fluid from the delay device I03, Fig. 11, through an outlet port I2I, a channel groove I22, Fig. 11, a channel groove I22a, Fig. 14, and channel I23, Figs. '1, 14. From the annular groove I20 short channel grooves I24, I25, Figs. '1, 14 extend respectively in opposite axial directions to effect communication between the groove I20 and the different ports I26, I21, Fig. '1, respectively as the lever H5 is moved in opposite directions. The ports I26, I21 respectively communicate through pipe channels I26a, I21a, Figs. 5, '1 with the ports 51, 56, Fig, 4, of reverser piston device 41. Simultaneously with movement of lever H5 to bring either port I25, I21, Fig. '7, into communication with the supply channel, the other port is connected to a drain, there being drilled holes 128, I29, Figs. '1, l4, suitably spaced for the purpose and communicating with an interior chamber or The port III is conannular groove I30 which is extended to the end of the sleeve valve II9 to drain into theinterior of the headstock. When hand lever H5. is in central position both the parts I26, I2"I- are connected to'the drain groove I30 there being. a plurality of drilled channels such as the channel I32, Fig.

14, for port I26 suitably positioned in the: valve sleeve II9 to'eifect' such connection, a'sim'ilar channelbeing provided for the port I21.

By reason of the construction of the sleeve" valve I .I9and the construction of thereyerser piston device, previously'described, itwill be apparent that the movement of lever I l5in either direction effects corresponding engagement of the reverser 6, while; a central position of the lever I I 5 eifects intermediate disengaged position Means are provided effective to shift the reverser to a position inter- I'rupting .the transmission to spindle 3ea'ch time a speed'change is-eifected, and. to return uthe reverser to its previous position, as determined by Fig; 11, of delay device I03. Port I2I normallya receives fluid from supply port II 0,'but in-the' operation of the device during speed change as. 30

flever I I5, upon completion of the speed change.

As previously'stated the supply of fluid to effect movement of thereverser is throughthe. port I2I,

previously described port I2I, as well'as port III,

is cut off from supply port I I and connected to the drain port I14. The result-is. to connect either active port 56 or 51 of reverser piston dethis the reverser piston device will again be supplled with'p'ressure fluid to shift reverser 6 to whatever position it previously occupied, unless the connection controlled by lever II5 has been changed during the speed change operation.

continuously supplied to the brake piston 6Ia, Fig.1 7,113 a direction to. urge the brake to braking .The brake 42, Figs. 6, 15, is controlled to be operative fromithe speed selector device during speed change and tube forced tobraking position whenever lever H5 is in'the position disengaging 1 reverser clutch. 6, as follows: Fluid pressure is position, the fluid supply being derived from pump 59 through port I06, Fig. '11, through the' channels I06a, I061), I06c, pipe connection I33, JFigs. 7; 11, and a drilled channel I34, Fig.7. The

braking pressure thus applied may be overcome, whereby torelease the brake, by the combined pressure of spring 45, Figs; 6, 15, and fluidpr'essure applied to the other side of piston 6Ia, at the leftehd, Fig. 7. Fluid'for' the latter purpose is supplied from port III of the delay device I03,-

' the channel gooves I31, I38, respectively positioned in the valve sleeve I I9 for communication with a channel I39in the difierent clutch engaged positions of'lever H5 and sleeve II9. From channel I39-the pressure fluid reaches piston 6I a "through channels, I40, I. In the disenga ed or central position of reverser control lever II5 the valve sleeve I I9 is in position, as shown in Fig.

to control the reverser6 from the spee'd'selector device/and which are" ply channels I31, I38, and to open the channel I39 to the drain I30 through a channel I39a in valve sleeve II9 the brake. v

Thus, whenever the reverser 6 is engaged, in either direction position the brake 42 is normally whereby to cause engagement of disengaged, but upon shiftingof the reverser to disengaged position brake 42 I engages.- Also, since the supply of brake disengaging fluid is through the port I II of delay device I03, it-will result that in each operation of speed changing the brake release supply will .be connected to' I drain port I I4, Fig. 11, and the brake will then be engaged temporarily irrespective ofthe position 'verser as previously described. But, as-later explained, the*brake is disengaged again before the reverser is re-engaged. A fluid operated detent member I33a, Fig. 7, is continuously pressedby fluid from the pipe channel I33 to engage suitable notches. such as I332) in the sleeve valve H9,

engage, reverser 5, the port I2I is opened to the drain H4,"during right hand movement of piston I01, before the port I. Therefore, during any speed change operation the reverser 6 is disengaged somewhat before the-brake 42 is engaged.

Following connection of port II I Fig. 11, to

\ the drain H4 during the right hand shifting of piston I0! the brake- 42 is immediately engaged,

thereby stopping rotation of spindle 3. Following' operation ofvneedle valve I09 to again connect portI II to the supply portIIII the brake 42 is released immediately and beforethe operation of any of the piston devices 63, 64, 65, there being restricting means operative on each of the piston devices but not on brake releasing means, as follows: Referring to Fig. 15 it will be seen that the fluid pressure from port II I of the delay devices are serially arranged for the piston device 63 to receive fluid only through device I42, while piston device 64 receives fluid through both de- 45 device I03 reaches the shifter piston devices 63, v 64, 65 only through devices I42, I42a, 142?). These vices I42, M211, and piston device 65 receives fluid 1 in the channel or supply groove 91b through which fluid reaches the piston devices and 65, the edges of the spring being closely but movably fitted to the sides of the channel groove, and the spring being of such form as to close the channel except as it is' sprung by the pressure of the fluid. The springs of each device I42, I42a, I42bare of material resistance, as. for instance 15 or 20 pounds. As will be seen from Fig. 15, the devices 63, 64, 65 will therefore operate in sequence as the pressure from delay device I03 rises; the device 63 operating when the fluid overcomes the flrst device I42, the device 64 operating when the pressure is twice as high whereby to overcome both the device I42 and H211, and device 65 operating only when the pressure is suflicientto overcome the three devices I42, I42a, I42b. Since brake 42 receives its pressure for brake release from port III, Fig. 11, exclusive of devices 2, Il2a, Il2b, as shown in Fig. 15, the brake will be released during any rate change prior to the operation of either piston device I3, ll, 65.

The fluid for the supply of the reverser piston device lI is derived through the channel I2I of the delay device III, Fig; 11, as previously explained. The relative positions of ports III and I2I is such that, following a rate change-operation, the left hand movement of piston III! will connect port III to the supply port III prior to the connection of port I2I for re-engagement of the reverser I. Brake l2 will, therefore be released prior to the re-engagement of reverser I.

To further control the reverser engagement, an engagement control device is provided, generally denoted by the numeral IlI, Figs. 15, 19. This device is connected serially in the line leading to the reverser piston device H from channel I2I of the delay device I 03, as indicated in Fig. 15, and therefore controls the operation of the reverser under all conditions whether operated from lever III or from the rate selector since, as previously explained, all the fluid for shifting the reverser is derived from the port I2I.

Device IlI includes a cylinder member 8, Figs. 8, 15, 19, fixed on the bottom of the housing member for the piston devices 63, Il, II and adjacent to the delay device I 03. A piston I", Fig; 19, provides an enlarged portion Illa and a relatively smaller portion IlIb, the latter operating in a sleeve 'IlI fixed in the cylinder bore. The intermediate portion of the piston Ill is exposed to a drain port I. The smaller area IlIb is exposed to the pressure derived from the port I2I and channel I22, Fig. 11 of delay device I03, through a port III. The larger area la is exposed through a port III and the channel I 220, Figs. 14, 19 to the pressure in the channel I 2I,'Fig. 14 which supplies the reverser piston device ll through the rotary control valve III.

1 A passage II2, Fig. 19, continuously communicates with the port III and channel I 224 at the one end, and at the other end provides a port III which is alternatively covered or uncovered by the small piston end IlIb as piston Il'I moves to right or left respectively, but even when the piston IlI is to the right some communication exists between the channels I22 and HM, the small piston end IlIb being of slightly reduced diameter, at 10 to provide a leakage path past the piston. A port -.IIl continuously communicates with channel I22 through port I50, and also with channel I22a through port III, but is prevented from passing fluid from port III to port III by a one-way valve device III, which may be of any suitable well known type, in this instance including a flat spring IIIa which clores the channel in the direction mentioned but yields to permit substantially free flow of fluid from port III to III.

By reason of the construction of device I as Just described the reverser piston device 41 will operate to immediately disengage the reverser, as previously described, as a-first step in the operation of rate change, the clutch engaging pressure being drained from the supply channel I 22a through the one-way valve III, Fig. 19, port III, channel I22, and port I2I and drain port I of delay device III, Fig. 11.

The piston Ill of control device Ill normally stands to the right in 19,.heing forced to this position by the relatively large area exposed at the left piston end. When the fluid is drained from channels I22, I22a, during rate change, the

piston Il'I temporarily remains to the right. But as fluid pressure is restored to channel I22. following a rate change, the piston I01 immediately moves to the left, because there is then no pressure on the larger left end. Such initial movement of the piston builds up an initial pressure in the port III and channel I22a, but the initial pressure is less than the pressure in channel I22 in the same proportion as the area of end Illb is less than the area of end Illa. The initial pressure for operation of reverser piston device l1 and the reverser I is therefore relatively low. The pressure in channel I22a is, however, gradually increased, by leakage through the restricted passage provided by the reduced piston diameter at IlIIc, until it becomes equal to the pressure in channel I22 and the reverser clutch plates are then .exposed to the full operating pressure.

At some intermediate point in the increase of pressure Just described, where the pressure on the larger end Illa of piston I", Fig. 19, overbalances the pressure on the smaller end I Hi), the piston I" again moves to the right to take up its normal operating position. This right hand movement also operates to slow down the equalization of pressures in channels I22, I22a because the right hand movement increases the length of the restricted passageway at IlIc and therefore reduces the rate of flow of the pressure equalizing fluid.

For regulation of the period required to build up the pressure in channel I22a, Fig. 19, there is provided a screw I II which is adjustable to control the position of an abutment piston III. The piston III is forced against screw III by fluid pressure, and provides an abutment determining the extent of the right hand movement of piston I 41. The farther piston IlI stands to the right, Fig. 19, following movement to the right during the equalization of pressure between passages I22, "211, the longer the equalizing operation will require.

By reason of the construction described the device I has no eflect upon the disengagement of the reverser I, but during engagement of either reverser clutch II, Il after interruption the device operates to start the transmission under initially reduced an d gradually increasing pressure, thus starting the gears slowly under partial power to assist engagement thereof during a rate change operation and, in any engagement or reversal, operating to avoid shock by gradually overcoming the inertia of the driven train.

The sequence of operations involved in a rate change operation is as follows: Assuming that the lever III, Fig. 16, is in a position to engage reverser I, and that the desired new spindle speed is for the same direction of spindle rota tion. In such case the only manual operation required is to rotate the selector in either direction by manipulation of the handles II of selector II until the desired new spindle speed, as listed on chart II, is in registry with the indicator I2. During such rotation the poppet valve III of the delay device I03, Fig. 11, will be opened each time the cam 86 passes through a position intermediate the notches "a, and as soon as the poppet valve is flrst opened the piston It! starts to move tothe right, Fig. 11, thereby connecting port I II to drain I whereby to effect a shift of reverser piston device l1 and reverser l to intermediate motion interrupting position. Slightly later in the right hand movement of piston III of device I" the-port III is alsoopened to. the

drain' H4, thereby immediately eflepting a braking position of brake 42 to stop spindle I. Upon the selector chart arriving at the desired speed position the poppet valve ill of device I03 re-' mains closed and fluid flows through needle valve I09, Fig. 11, to shift piston I01 to its normal left hand position. During such left hand shift it flrst occurs that port III is opened to pressure fluid, whereupon the spindle brake 42 is immediately released, and as the pressure rises in port Iii the rate change shifter piston devices 63, 64, 65 are subjected to pressure in the order mentioned, the sequence being controlled by the devices l42,'l42a, l42b. 5 The new speed position of the selector device 1| effects a new position combination of the poppet valve cams and poppet valves associated with the piston devices 6 3, 64, 65, and therefore the rise'of pressure in -"these devices willurge go the pistons to effect a corresponding new position combination, but only those pistons will be moved where a poppet valve closed in the previous speed position has been opened in the new speed posi-' tion.

Very shortly after pressure fluid has been admitted to the'port ill, Fig. 11, the continued movement of piston I01 to the left also opens port Hi to pressure fluid, which is applied to the reverser piston device 41 through the control device I45 and the direction control valve H9 to effect engagement of the reverser 6. Since the direction control valve H9 has not been moved during the rate change operation the result is to engage reverser 8 to effect the'same spindle direction as before the rate change, but

by reason of the operation of the device I 45 to initially restrict the'fluid pressure to relatively low value, as previously explained, the reverser engagement is withoutjar or shock.

40 Following the release of brake 42 in the operation described above the spindle train is free to turn, the slight friction of the disengaged reverser clutch plates will ordinarily turn the train slowly to assist engagement of the various gears to be shifted during a rate change, but in any event the gears will start to'turn as soon asthe reverserstarts to engage, and during the interval while device I4! is effecting the building up of the reverserpressure'the gears will rotate 5o slowly to insure meshing of the engaging gears.

It is to be noted thatthe construction and control of reverser-interruptor 6 is such that the device acts as an overload device limiting the power applied to the spindle and feed trains, and

b5 productive of various other useful results. Gertain features thereof are more particularly pointed out in a co-pending application Serial No. 130,273, flied March 11, 1937, and allrights to the'structure there claimed are specifically 6o reserved, as well as to.-certain other features shown or described in" this application, but claimed in one or the otherof the several copending applications mentioned herein.

What is claimed'is:

. 1. In a machine tool the combination of a transmission train including an impositive clutch movable between driving and motion interrupting positions and a shiftable rate change device driven through said clutch, a plurality of power 70 operable shifters respectively for said clutch and rate change-device, a power train connectible with said shifters, control means including means substantially simultaneously connecting said power train for operation of said rate change 45 device shifter and clutch shifter, and means delaying. subsequent movement of said clutch to driving position to effect a period of partial clutch engagement.

2. In a machine -tool the combination of a transmission train including an impositive clutch i movable between driving and motion interrupting positions and a shiftable rate change device driven through said clutch, a plurality of power operable shifters respectively for said clutch and rate change device, a power train connecti-, 10

ble with said shifters, control means including means substantially simultaneously connecting said power train for operation of said rate change device shifter and clutch shifter, means delaying subsequent movement of said clutch to driving 16 position, and means adjustable to determine the duration of the period of said delay.

3. In a machine tool having a transmission including a rate changer providing a plurality of shiftable speed change devices serially ar ranged, the combination of a plurality of 'power operable shifter devices respectively for the different speed change devices, a rate selector device including a chart having markings indicating various rates corresponding to different po- 5 sition combinations of said speed change devices and an indicator movable relative to said chart, a plurality of resistor devices respectively associated with the different shifter devices to effect different power requirements for operation of the different shifter devices, a power train connectible with said shifter devices through said resistor devices, and control means for the connection of said power train to operate said shifter device in accordance with the rela- 35 tive position of said chart and indicator.

4. In a machine tool having a transmission including a rate changer providing a plurality of shiftable speed change devices serially arranged, the combination of a plurality of fluid operable l0 piston devices respectively connected for the operation of different of said speed change devices, a rate selector device including .a chart having markings indicating various rates corresponding to different position combinations to of said speed change devices and an indicator movable relative" to said chart, a source of hydraulic pressure connectible with said piston devices, valve means operable from said selector device and controlling the connection of said pressure source to operate said piston devices in accordance with the relative positions of said chart and indicator, and a plurality of resistor devices respectively associated with different of said piston devices and collectively effective for 56 operation of the different devices at different pressures.

.5. In a machine tool the combination of 'a transmission including an impositive clutch movable between driving and motion interrupting positions'axrd-a plurality of shiftable rate change devices serially arranged, a plurality of power operable shifters respectively for said clutch and for different of said devices, a rate selector including a chart and indicator means movable relative to said chartya power train connectible for. operation of said shifters, control meansoperative upon relative movement of said chart and indicator means to connect said power train and shifters to shift said clutch to motion interrupting position, control means subsequent- -ly operative to connect said power train and shlfters'to shift said devices in accordance with the relative positions of said chart and indicator means, means later operative to connect said 7 power train and shifters to shift said clutch to driving position, and means operative to provide a substantial period of partial clutch engagement upon operation of said later operative means.

6'. In a machine tool the combination of a a plurality of power operable shifters ,respec- I,

tively for said clutch, for different of said rate change devices and for'said brake, a rate selector including a chart and indicator means movable relative to said chart, a power train connectible for operation of said shifters, control means operative upon relative movement of said chart and indicator means to substantially simultaneously connect said power train and shifters to move said clutch to motioninterrupting position and to engage said brake, dependently operable control means subsequently operative to connect said power train and shifters to effect a position combination of said rate change devices corresponding to the relative position of said chart and indicator and substantially simultaneously shift said brake to released position, control means later dependently operable to connect said power train and shifters to shift said clutch to engaged position, and means operative to effect a substantial period of partial engagement of said clutch upon operation of said later operative means.

'7. In a machine tool the combination of a transmission train including clutch means comprising engageable and disengageable friction surfaces, a piston device, a connection from said piston device for alternative engagement and disengagement of said surfaces, a source of pressure fluid, valve means adjustable for connecting said source and piston device to effect said alternative engagement and disengagement, and means operative in the valve connection effecting engagement of said friction surfaces to effect a substantial period of relatively low pressure between said source and piston device.

8. In a machine tool the combinat on of a transmission train including clutch means comprising eng ageable and disengageable friction surfaces, a piston device, a connection from said piston device for alternative engagement and disengagement of said surfaces, a source of pressure fluid, valve means adjustable for connecting said source and piston device to effect said alternative engagement and disengagement, means operative to effect a period of relatively low pressure engagement of said friction surfaces following the valve adjustment effecting engagement thereof, and means adjustable for changing the duration of said low pressure period.

9. In a machine tool transmission the combination of clutch means including engageable and dlsengageable friction surfaces and a rate change device including elements shiftable to a variety of position combinations respectively productive of different speeds, a power train, a first controller operative for effecting a connection of said power train to shift said elements, effect a predetermined position combination thereof and to dependently subsequently engage said friction surfaces,- a second controller operable to connect said power train for selective alternative engagement or disengagement of said advance friction surfaces independently, of a shift of said elements, and means operative in the engagement of said friction surfaces from one of said controllers to effect a substantial period of partial engagement thereof.

10. In a machine tool transmission the combination of clutch means including engageable and disengageable friction surfaces and a rate change device including elements shiftable to a variety of position combinations respectively productive of different speeds, a source of pressure fluid, piston devices connectible with said source for alternative engagement, or disengagement of said surfaces and for effecting different of said element position combinations, a first control means operative for connection of said source and piston devices to shift said elements to effect, a predetermined element'position combination and dependently subsequently to engage said friction surfaces, a second controller operative to connect said source and piston devices for selective alternative engagement or disengagement of said friction surfaces independently of a shift of said elements, and control means operative during engagement of said friction surfaces from one of said controllers to effect a substantial period of relatively low pressure engagement of said surfaces.

11. In a machine tool transmission the combination of clutch means including engageable and disengageable-friction surfaces and a rate change device including elements shiftable to a variety of position combinations respectively productive of different speeds, a source of pressure fluid, piston devices connectible with said source for alternative engagement or disengagement of said surfaces'and for effecting different of said element position combinations, a first control means operative for connection of said source and piston devices to shiftsaid elements to effect a predetermined element position combination and dependently subsequently to engage said friction surfaces, a second controller operative to connect said source and piston devices for selective alternative engagement or disengagement of said friction surfaces independently of a shift of said elements, pressure reducing means associated with said source connection to effect a substantial period of relatively low pressure engagement of said surfaces upon engagement from one of said controllers, and adjusting means controlling the operation of said pressure reducing means to determine the duration of said low pressure period.

12. In a machine tool the combination of trans-- mission mechanism including motionv reverser means comprising a plurality of sets of engageable friction surfaces respectively -for opposite driving engagement and having a motion interrupting position and a rate changer comprising a plurality of speed change elements shiftable into a variety of different position combinations respectively productive of different speeds, power operable devices respectively connected for shifting said reverser means and for shifting said elements, power means connectible with said power operable devices, a selector movable to a variety of positions respectively corresponding to different of said element position combinations, means operative in each of said positions-of said selector to connect the power mea s with some of said devices to effect the elemen position combination corresponding to the selector position, means operative upon movement of said selector from one to another of said positions to change 13. In a machine tool the combination of transmission mechanism including motion reverser ,gageable friction surfaces respectively for oppoand a brake alternetively operative and release said member, power opsaid clutch to restrain the combination of rate change means including elements shiftable to various position combinations respectively for difierent rates, driving means for said rate changer including a clutch device comprising engageable friction members, a rate selector adjustable to various positions respectively corresponding to different of said position combinations, means operable in accoi'tlance with selector adjustment from one to another of its positions for shifting said elements to a corresponding position combination, a fluid operable piston device connected for engagement of said friction members, a pressure fluid source,

channel means connectible between said source and piston device including valve means alternatively adjustable for member engagement or disengagement, means operative from said selector or operation of said valve means to disengage and subsequently to engage said members, and means associated with said channel means to limit the rate of engagement of said members,

said rate limiting means being inoperative during member disengagement whereby dlsengageo ment occurs at a relatively rapid rate.

WERNER IRVING SENGER. VIGO VON K'RDGH SUNDT. 

